Forced-lubrication apparatus



Sept. 2o; 1927.

. 1 1,642,373 v C. H. CLAUSEN v -FORCED LUBRICATION APPARATUS n Filed March 13, 1925 3 Sheets-Shea?l l sept. 2051927.

C. H'. CLAUSEN FORCED LUBRICATION APPARATUS Filed March 13; 1925 5 Sheets-Sheet 2 Jia (f'efL Z0 7 C. H Clar/cae/z Sept. 20u92?.

c. H. CLAUSEN FORCED LUBRICATION APPARATUS Filed'March l5', 1925 3 Sheets-Sheet [nden/41 'QH-Cinese Patented Sept. 1Z0,v 1927.

Unir-En.. sra.

canili HERMAN CLAUSEN, or

sotvnsnone, SWEDEN, asssnoaro P nrnnraxprrn is'oneefn'iv CENTRALSMRJNING, or soLvEsBoRe,`swnDEN, A` oonrona'rronior swnnniv.

Appncauoa ined nai-ch is, 1925,` serial The subject of this invention is a drivingA and guiding device. for the pump pistons in forced lubrication apparatus andthe object of the invention is to simplify this device to the greatestpossible extent, without depre ciating the function orthe veffect, ofl theV apparatus, and thus to obtain acheap appa-I ratus. 4 It is already known to drive a pump piston'by the means'of an eccentric orcam disc which by the inter'mediaryof a fork-shaped party acts upon the piston' or its rod, thereby causing a reciprocating motion of the-piston. It is furtherv known to construct valveless pumps, in which the pump cylinder is alternately'brought in communication with suc tion and pressure conduits by rotating the piston about its longitudinal axis and providing the same with connection channels, so that the piston in addition to itsordinary function also acts asrot-ary valve. In these lin-own devices however very complicated mechanical contrivances for obtaining the double (the reciprocating: andv the rotary) motion of the piston had to be adopted, andV the chief object of the invention is toV accomplish a` far reaching simplification of the driving device.y This, according to the invention, is obtainedin two manners perL fectly alike as to the principle but somewhat departingfrom each other with respect to the mechanical execution', viz

(a) By arranging in the apparatus a driving cylinder disposed eccentrically relatively to the axis of rotation, the eccentricity of said cylinder causing the reciprocating motion of thepiston, while grooves arranged in this cylinder inclining toward the axis of rotation and in cooperation with a crank-pin or the like fitted tothe pump piston bring about the rotary motion, and i (Z9)v By arranging in the apparatus a driving cylinder of whatever "external form, which may be cogaxial in relation to the axis of rotation, and providing this cylinder with obliquely disposed grooves for causing y the rotary motion of the pistons in the same manner as before, but which grooves are pro'- vided with a bottom eccentric'ally disposed in relation to the axis of rotation andprefer'- ably inthe form of a cam disc, so that this groove 'bottom on account. of its position relatively to the pump piston will cause the reciprocating motion of the latter.` In this roncnn-nnenrcarronArraaafrns.

N. 15,409, in sweden July s, 1924( caseV the craiilrfpin connected to the piston and engaging the groove may preferably be substituted by a mechanicalequivalent, viz,` an eccentric. i

rllhus the difference between these tw mechanical embodiments ofthe invention is this that in the'formencas it is'th'e eccen-i tricityof the driving cylinder Lwhich brings about the reciprocating motion 'of' the pis-` tons, while in the 'latter case the bottoms of the grooves are causing'same motion, and here theexternal form of the cylinder and'its disposition relatively vto the axis of rotation is of-no infiuencemfor the function ofthe pump. H f The invention is more fully explainedy in the following -descriptionreference being had tothe accompanying drawings, in which Figs. l andv 2 show a forced `lubrication apparat-us adapted for lfour lubricating places, and executed'in accordance with the embodiment indicated above as (a), in a transversal and longitudinal section respectively.- Fig. 3 shows on a larger scale a detai-l'of--the driving cylinder in a transversal section,

andv Fig. i shows likewise on a larger scale a pump' piston in a" lateral view. "Figs '5 and' 6 show a horizontal projection anda ltransversal section respectively of Fig. 4;

Figs. 7 and 8 show in a like manner asin Figs. 1 and 2 a forced lubrication apparatus executedy in accordance with the embodiment indicated above as (b). i .Y

'In thevembodiment according to Figs. l to 6 the numeral 1 designates an oil container, in which isjournalled a driving shaft 2 connected to a suitable source ofpower and in which there are further arranged oilI pumps. 3 of a numberin agreement` to the number of lubricating places, said oil'pumps having. suction channels `44 embouching within the container near its bottom and pressurel n channels passing through the wall of the container and adapted to be connected ina suitable manner with-oil conduits.

Each pump 'has' a fixed guide, preferably a rode, an arcuated strap 7 being displaceably arranged thereon, the one branch of the strap embracing with a fork-shaped partk 8 the pump piston immediately below a fiange or head'9 fixed thereto, and the other branch of the strap *provided withv a Screw 10 having a Vcorresponding' flange or ahead 11. On-the driving `shaft 2 there is; eccentrically ar..-`

ranged a cylinder 12 disposed between the heads 9 and 11, and when rotating the driving shaft the pump pistons receive by the intermediary of the eccentric cylinder 12 a reciprocating motion, the length of stroke of which is variable by adjusting the screws 10. The heads 9 are provided with a crank-pin 13 pointing toward the shaft 2, said crankpin extending into an endless groove llin the cylinder 12 disposed obliquely relatively to the axis of the driving shaft, so that by this means the pump pistons in addition to the above stated reciprocating` motion also receive a rotary motion. f

In order that the pumps may work in a theoretically correct manner, that is to say that the inlet and outlet of the pump cylinders register correctly with the suction and pressure channels respectively, it is of importance, that the rotation of the piston takes place at the two ends of its stroke or,

inV other words, in those positions of the piston, in which this has no appreciable axial motion'- To accomplish this, the grooves 14 have two straight. parts disposed at right angles relatively to the axis of the shaft intwo different planes (see Fig. 2) and these straight groove parts are arranged relatively to the eccentricity of the cylinder 12 in such a manner,that they correspond to resting periods in the axial motions of the pistons. The straight groove parts are arranged at such a distance axially from each other that they 'correspond to a rotation of the pistons of 90, in consequence whereof the suction inlet and pressure outlet of the pump cylinder become disposed diametrically opposite to each other, so that they may be executed in form of a bore-hole passing straight through the cylinder, as disclosed in Fig. 1, and by this means the manufacture is furthermore simplified. The straight groove parts are connected with each other with oblique groove parts, which cause the rotation of the pump piston, the one inthe one direction Vand the other in the other direction.

Though the grooves being carriedout in the manner above described it should be clear, that for reason that the oblique groove parts cannot actually be arranged accurately axially along two opposite generatrixes for the cylinder 12, the function of the pumps will not betheoretically correct, if the cylinder 12v has a true eccentric form, for in such case the pistons receive just as well an axial displacement simultaneously with the rotation.A To avoid this, the cylinder 12 is not made accurately eccentrical but receives a cross-sectionaly forni as 'disclosed in Fig. 3. This form has arisen in the following manner -The outer mantle of the cylinder has been divided up' in four bows opposing each other in pairs, of which the two bows 15 and 16 corresponding to the greatest and smallest eccentricity are true circular arcs having the axis of the shaft 2 as centre, while the two remaining` bows 17 and 18 which connect and smoothly go overv into they first named bows are preferably also circular arcs but having a centre eccentrically disposed in relation to the axis of the shaft 2. The bows 17 and 18 need not necessarily be circular arcs but may be constituted of other aliined curves. `The bows 17 and 18 correspond to the straight parts ofr the grooves 14: and the bows 15, 16 to the oblique parts, and it should be clear, that on account of the described eccentric or, more correctly expressed, cam form of the cylinder 12 the pistons are not subjected to any axial displacement during their rotation.

The pump pistons (Figs. l and 6) are provided with an axial channel 19 opening into the pump cylinder and two channels 2O and 21 emerging from the channel '19 at an angle of 90 between. When rotating the piston, the channels 20and 21 are alternatelybrought in communication with the suction and pressure channels' 4 and 5 respectively. Tn order to keep the communications open during the axial displacement of the piston axial grooves are arranged in the outer surface of the piston at the embouch'ments of the channels 20 and 21.

Tt should be obvious, that the embodiment above described may bevaried in many respects. Thus, for each pump one may arrange a separate 'driving cylinder provided with grooves, which cylinder, for example in form of a collar, is pushed upon and fixed to the shaft in a suitable manner, for example with set screws. The manufacture of the apparatus in this manner embodies sev-v eral advantages, because the driving shaft and the members connected thereto may more easily be adapted to agree with varying members of pumps in cach apparatus and further, in apparatus having a large number of pumps, the load may be evenly distributed by placing the eccentrics at different angles in relation to each other. Further the forks 7nee'd not he displaceably arranged on the rods 6 but could be securely fastened thereto, if the rods for example are displaceable in guides (bore-holes), and the part 8 may entirely embrace the piston or its rod.

In the embodiment shown in Figs. 7 and 8 like reference numerals as in Figs. 1 to 6- are used for like parts. A convenient number of pumps o arranged in the oil container 1, are `driven from the common shaft 2 by means of straps 7--8 embracing the shaft. These straps are displaceably mounted onguide rods 6 and attheir upper part provided with heads 11 adjustable by means of screws 10 for controlling the length of stroke of the puinppiston and thus the effect ofthe pump. Y

Instead of having the above described ioe Y lli) crank-pin 13 the pistons in this case are proline substantially parallel to the movement vided with a head in the form of a disc 22 at right angles and eccentrically disposed relatively t-o the axis of the piston, and it is this eccentric head that directly causes the rotation of the piston, which latter thus simultaneously serves as rotary valve. By this means the manufacture of the piston becomes further simplified.

'Io accomplish the rotation of the pistons the eccentric head 22 engages in grooves .2S-corresponding to the grooves 14 in the embodiment first described-and these grooves are obliquely disposed in relation to the axis of driving shaft in a cylinder 24, corresponding to the cylinder 12. The outer form of this cylinder 24 is immaterial for the invention but is shown in the drawing to be of cylindrical form. The bottom of the grooves 23 is eccentric relatively to the axis of the driving shaft or has the form of a cam disc having the same properties as the cam-shaped driving cylinder l2 above described, and it is this eccentric groove bottom that causes the axial displacement of the pistons when rotating the shaft.

What I claim and desire to secure by Letters Patent is apparatus comprising a pump with a pump piston, a driving shaft, a cylinder mounted eccentrically thereon and formed with an endless groove in part in a plane at right angles to the axis of t-he shaft and in part in a plane oblique to said axis, a strap partly surrounding the cylinder, one end of the strap cooperating with the pump piston to rotatably carry t-he latter, a crank carried by the pump piston beyond the strap'with the crank pin engaging in said groove in the cylinder, and means for guiding the strap against other than a reciprocating movement in a of the pump piston.

2. A driving device for a forced lubrican tion apparatus comprising a pump with a pump piston, a driving shaft, a cylinder mounted eccentrically thereon and formed with an endless groove in part in a plane at right angles to the axis of the shaft and in part in a plane oblique to said axis, a strap partly surrounding the cylinder, one end of the strap cooperating with the pump piston to rotatably carry the latter, a. crank carried by the pump piston beyond the strap with the crank pin engaging in said groove in the cylinder, means for guiding the strap against other than a reciprocating movement in a line substantially parallel to the movement of the pump piston, and means carried by the end of the strap opposite that end connected tothe piston to bear upon said cylinder in substantial alignment with the piston.

3. A driving device for a forced lub-rication apparatus comprising a pump, a pump piston therein having a head, a driving shaft, a cylinder mounted eccentrically on the driving shaft and formed with a groove having a port-ion at right angles to the axis l. A driving device for forced lubrication.` of the Shaft and a' portion Oblique to' Such axis, al strap guided for reciprocating move ment in a line substantially parallel to the movement of the piston and having its respective ends above and below the cylinder in substantial alignment with the piston, the lower end of the strap being connected to the piston below the head thereof to rotatably carry the piston, a crank pin on the-,piston head adapted to seat in said groove, and an adjustable head carried by the upper end of the strap to bear on the cylinder.

In testimony whereof, I have signed my name to this specification.

CARL HERMAN CLAUSEN. 

